Rotary pump and engine



G. F. MOORS. ROTARY PUMP AND ENGINE. APPLICATSON FILED NOV. 5. 1918.

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Patented Feb. 28, 1922.

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GEORGE F. MOORS,

COMPANY, OF ST. LOUIS, MISSOURI, A

OF ST. LOUIS, MISSOURI, ASSIGNOR TO RECI'P-ROTO ENGINE CORPORATION OF DELAWARE.

ROTARY PUMP AND ENGINE.

full, clear, and exact description, reference.

being had to the accompanying drawings, forming a part of this specification.

My invention relates to improvements in rotary pumps and engines, and more particularly to a rotary machine of this kind provided with means for controlling theadmission and discharge of fluid. The structure herein. disclosed comprises a cylinder having inlet and outlet ports, and an eccent-rically mounted piston movable in the cylinder. The main object of the invention is to produce a very simple and highly efficient means for controlling the flow of fluid through the cylinder. In the preferred form of the invention, at least one valve element.

is carried by the eccentrically mounted piston, and in response to the peculiar movements of the piston, this valve element cooperates with another valve element to control the flow of fluid through one of the ports. More specifically stated, the structure about to be described comprises an eccentrically mounted piston and a pivot from which the piston oscillates in the cylinder; This piston moves away from the inlet port and toward the outlet port to provide for the admission and discharge of thefiuid, and owing to the peculiar-manner in which it is mounted in the cylinder, the piston also moves from an extreme position near the the outlet port to an 'nitial position near During this last mentioned movement of the piston, at least one of the ports should be closed to prevent free communication between the ports. Therefore, the cylinder is preferably provided with inlet and outlet valve elements and corresponding valve elements are preferably carried by the eccentrically mounted piston, said valve elements being arranged to properly cooperate with each other while the piston is moving from its extreme position to its initial )osition. The main features of novelty lie 1n the combination and arrangement of valve elements whereby the ports are properly opened and closed in response to the movements of the eccentrically mounted piston.

Specification of Letters Patent.

and

Patented Feb. 28, 1922.

Application filed November 5, 1918. Serial No. 261,258.

Fig. I is a side elevation, partly in section, illustrating a rotary-pump constructed in accordance with the invention, one of the cylinder heads being removed.

Fig. II is a vertical section taken approximately through the center of the pump shown in Fig. I.

Fig. III is a diagrammatical view showing the piston in the position it occupies immediately before all of the out-going fluid is expelled through the outlet port:

Fig. IV is a view similar to Fig. III, showing the piston in a different position.

To illustrate the invention I have shown a duplex pump comprising a cylinder A provided with heads 1 and also having a partition 9 (Figs. I and II), whereby it is divided into two compartments designated B and B. The partition 2 has an extension 2' which lies between an intake chamber 3 and a discharge chamber 4. Each of these chambers is adapted to communicate with the cylinder compartments on opposite sides of the partition 2-2.

A rotary'powershaft 5, located at the center of the double cylinder, is provided with a square portion 5" which lies within the cylinder compartments, and with round portions which extend through stuffing boxes '6 (Fig. II) in thecylinderheads. This rotary shaft extends through the partition 2, as shown in Fig. II.

Each compartment of the double cylinder is provided with a piston and with certain other elements which I will now describe. Each piston P is an annular member mounted on an eccentric E, and each eccentric is rigidly secured to the square portion of the rotary power shaft. Each eccentric E is also recessed to receive a fixed wedge 7 engaging one of the fiat faces of the power shaft and an adjustable wedge 8 cooperating with said fixed wed 'e. The adjustable wedge 8, as shown in ig. II, is interposed between the fixed wedge 7 anda portion of the eccentric E. 9 designates a bridge plate engaging shoulders on the eccentric and wedge 7, respectively, and 10 is an adjusting screw passing through the bridge plate and screwed into the wedge 8. By adjusting the screws 10 the wedges may be tightened to firmly secure the eccentrics to the power shaft. I

The flat side faces of each annular piston P contact with the oppositely disposed flat faces of the cylindrical compartment in which it is mounted, and to prevent leakage above the piston the latter is connected to an abutment head 12 fixed to an arm 13, the latter being pivotally supported by a rod or shaft 14. Each pivotally mounted abutment head 12 is equal in width to the adjacent piston P. In other words, the abutment head and piston are co-extensive relative to the axis of the power shaft 5. The abutment head, therefore, contacts with a cylinder head 1 and the partition 22, so as to prevent free communication between the intake chamber 3 and the discharge chamber 4.

The means for forming a fluid-tight pivotal connection between the piston P and abutment head 12 preferably comprises a tubular member 15 extending from the top of the piston, a pivot rod 16 mounted in said tubular member, and screws 17 connecting the abutment head to said pivot rod. These connecting screws pass through slots in the tubular member 15, as shown in Figs.

. I and II, so as to allow the piston to oscillate about the axis of the pivot rod 16. The bottom face of each abutment head 12 conforms to the curvature of the adjacent tubular member 15, and the desired fluid-tight joint can be obtained by tightening screws 17, thereby forcing the abutment head into engagement with the tubular member 15. Plugs 18, located above the abutment heads, may be removed to permit the application of an adjusting tool to the heads of the screws 17. Each abutment head 12 oscillates about the axis of the pivotal connection 14, and preferably contacts with a stationary body of anti-friction metal 19, such as Babbitt metal, secured adjacent to the intake compartment 3, as shown in Fig.I. The contacting faces of the abutment head and Babbitt metal are concentric with the pivotal connection 14.

20 and 21 designate inlet and outlet ports formed at opposite sides of theabutment head 12. These ports may be closed by valve elements on the piston and cylinder, as shown in Fig. I, and they may be opened to provide for the admission and discharge of fluid as shown in Figs. III and IV. In the structure I have shown to illustrate the invention, the ports are opened and closed by means of fixed inlet and outlet valve elements 22 and 23, respectively, which project into the cylinder at points adjacent to the ports, said ports being formed between the valve elements. The annular piston is provided with valve elements 21 and 25 adapted to cooperate with the valve elements 22 and 23. The valve elements 24 and 25 may be formed within the circumferential line of the piston, and the axis of the pivot 16 may be formed on slid circumferential line.

Each eccentric E turns with the power shaft 5 as indicated by curved arrows in Figs. I, III and the eccentric movement charge of fluid. When the parts occupy the positions shown by full lines in Fig. I, both ports are closed, and a continued movement of the eccentric will locate the annular piston in the position shown by Fig. IV, wherein both ports are open and the piston con,

tacts with the left side of the cylinder at a point near the inlet port. As the eccentrlc continues its rotary movement, the annular piston will remain in contact with the cylinder, and the point of contact will gradually approach the outlet port. Fluid at the right hand side of the piston is thus expelled through the outlet port, and at the same time fluid is admitted through the inlet port 20 as indicated by arrows in Figs. III and IV. When the iston reaches the position shown by Fig. III there will be very little fluid between the piston and the outlet port 21, while a very large body of fluid will lie at the left side of the piston. A continued movement of the eccentric will locate theannular piston in its highest position (Fig. I) wherein the inlet and outlet ports are closed by the lapping valve elements 22, 23, 24 and 25. while the piston is moving to the left so as to displace the body of fluid in the cylinder. It is important to observe that at least one of the ports should be closed at this time, for the annular piston is in a dead or neutral position and its peripheral face does not contact with the cylinder. If both ports 2021 were open during this dead or neutral period, the back pressure of the fluid in the outlet chamber 4 would cause the fluid to flow backwardly through the cylinder. Even a. momentary flow of this kind would result in a loss of power, and a shock or jar would occur when the backward flow is suddenly stopped by the subsequent engagement of the piston and cylinder.

Immediately after the piston occupies the neutral position shown by Fig. I. it again reaches the position shown by Fig. IV and continues in motion to discharge the fluid through the outlet port.

D I will now describe the peculiar manner in which the valve elements cooperate with each other to open and close the inlet and outlet ports. Fig. III shows the positions of the parts immediatelybefore the outlet valve 23. 25 is closed. At this time liquid is passing through the open outlet port 21. and the outlet valve element. 25 graduallv approaches the element 23. The point of contact between the piston and cylinder gradually approaches the outlet port, but the outlet valve is not closed until all of the outgoing liquid is expelied between the adjacent valve elements. A study of F ig. III

the position shown will show that the annular piston is moving upwardly in response to the rotary movement of the eccentric E, and that it is also moving to the left on the axis of the pivot 16. This twofold movement brings moving valve element 25 toward the fixed valve element 23, and causes all of the outgoing liquid to be expelled before the valve elements contact with each other. .By closing the outlet valve in this manner, I avoid trapping of the outgoing liquid between the piston and the outlet valve elements, thereby avoiding undue stresses and noise which would otherwise be caused by a premature closing of the outlet valve. This valve is positively closed at the most favorable moment, immediately after all of the outgoing liquid has been discharged between the valve elements. Communication between the cylinder and the outlet chamber 1 is thus closed as the piston moves to its highest position, shown by 1 ig. 1.

Immediately before the outlet valve closes the inlet port 20 is wide open, the inlet valve elements 24 and 22 being widely separated as shown in Fig. III, so as to permit the incomin liquid to pass freely into the cylinder; 'owever, as the piston continues in motion, the inlet valve element 24 gradually approaches the fixed valve element 22. When, the piston reaches itshighest position, shown by full lines in Fig. I, both valves are closed to prevent communication between the cylinder and the inlet and outlet chambers. At this time the piston is dead, ormomentarily ineffective, so far as its pumping function is concerned, and it'is moving toward the inlet side of the cylinder.

The movement of the piston from the position shown by Fig. III, wherein it contacts with the outlet side of the cylinder, to the position shown by Fig. IV, where it contacts with the inlet side, results in a displacement of the liquid in the cylinder, and this piston movement is obtained without placing the inlet port in free communication with the outlet port.

When the annular piston is passing from by Fig. III to the position shown in Fig. IV. it occupies its dead or neutral position wherein both valves are closed, as shown in Fig. I, and during this period the piston moves quickly on the axis of its pivot 16, thereby quickly actuating the movable valve elements and at the same time moving rapidly from the outlet side of the cylinder to the inlet side. This quick movement is obtained without materially raising or lowering the annular piston and without materially changing the location of the pivot 16. To clearly understand this point, several conditions illustrated by Fig. I should be carefully noted. The two centers of the eccentric are in alinement with the center of The piston turns quickly the fixed valve elements.

the pivot 16, and the piston and eccentric are in their highest position. Consequently, the movement of the eccentric on the axis of shaft 5 quickly forces the piston to the left. on the pivot 16, but the pivot itself moves only a very slight distance during this period. This being true, it is an advantage to make the faces of the valve elements 22, 23,24: and 25 conform approximately to arcs drawn from the center of the pivot 16. are formed in this manner the movable valve elements will cooperate most effectively with One of the objects is to prevent free communication between the inlet and outlet ports during the neutral period wherein the piston occupies the position shown by full lines in Fig. I. At this time the eccentric is turning with the power shaft 5, as indicated by the long arrow a in Fig. I, but the annular piston is turning on the pivot 16 so as to move the valve elements 24 and 25, as indicated by the short arrows b and c in Fig. I..

The faces of the valve elements are approximately concentric with the pivot 16, and since the pivot is not materially shifted during the neutral period the valves will prevent free communication between the inlet and outlet ports during this period. Furthermore, the valve elements formed and arranged as herein shown will open and close at the most favorable moments.

Claims generic to this application and to my copending application Serial No. 340,17 9, filed Nov. 24:, 1919, are incorporated in the latter application.

I claim:

1. The combination of a cylinder provided with inlet and outlet ports, a piston in said cylinder, said piston beingv smaller in diameter than the internal diameter of said cylinder. oscillates in said cylinder, a rotary memher on which said piston is eccentrically mounted so as to cooperate. with the circular inner face of the cylinder, the eccentrically mounted piston being movable away from the inlet port and toward the outlet port to provide for the admission and discharge of fluid, said eccentrically mounted piston being also-movable, on the axis of said pivot, from an extreme position adjacent said outlet port to an initial position adjacent said inlet port, and means for closing one of said ports during the last mentioned movement of the piston, said means comprising lapping valve ele ments on said piston and cylinder, and the cooperating faces of said ments being approximately concentric with said )ivot.

2. he combination. of a cylinder provided with inlet and outletportg a, piston If the valve faces contacting a pivot from which said piston in said cylinder, said piston being smaller in diameter than the internal diameter of said cylinder, a pivot from which said piston oscillates in said cylinder, a rotary member on which said piston is eccentrically mounted so as to cooperate with the circular inner face of the cylinder, the eccentrically mounted piston being movable away from the inlet port and toward the outlet port to provide for the admission and discharge of fluid. said eccentrically mounted piston being also movable, on the axis of said pivot, from an extreme position adjacent said outlet port to an initial position adjacent said inlet port, and means for closing said ports during the last mentioned movement of the piston, said means comprising valve elements adjacent to said port-s and valve elements carried by said piston, said pivot being located approximately on the circumferential line of said piston, and'the cooperating faces of said valve elements being approximately concentric with said pivot.

3. The combination of a cylinder, a piston in said cylinder, said piston being smaller in diameter than the, internal diameter of said cylinder, a rotary member on Wl1lCl1 Stll(l piston is eccentrically mounted so as to contact with the circular inner face of the cylinder, anabutment extending from said piston, a pivotal connection uniting said abutment and the eccentrically mounted piston. said cylinder having inlet and outlet ports at opposite sides of said abutment, said eccentrically mounted piston being movable away from said inlet port and toward said outlet port to provide for the admission and discharge of fluid. said eccentrically mounted piston being also movable on the axis of said pivotal connection from an extreme position adjacent said outlet port to an initial position adjacent said inlet port, and means for closing said ports during the last mentioned movement of said piston, said means comprising a pair of valve elements carried by said piston and located at opposite sides of said abutment, and said cylinder being provided with a pair of valve elements which cooperate with the aforesaid valve elements while the piston is moving on said pivotal connection from the extreme position to the initial position, the axis of said pivotal connection being approximately on the circumferential line of the piston and the cooperating faces of said valve elements being approximately concentric with said pivotal connection.

4. The combination of a cylinder, a rotary shaft at the axis of said cylinder, an eccentric arranged in said cylinder and fixed to said shaft, an annular piston mounted on said eccentric so as to contact with the circular inner face of the cylinder, said annular piston being smaller in diameter than said circular inner face, an abutment movable into and out of said cylinder, said abutment and piston being co-extensive relative to the axis of the cylinder, and a pivotal connection whereby said annular piston is connected to said abutment, said cylinder having inlet and outlet ports at opposite sides of said abutment, said cylinder also having inlet and outlet valve elements at points adjacent to said ports, said annular piston having valve elements which cooperate with the aforesaid valve elements in opening and closing the ports, and the cooperating faces of the several valve elements being approximately concentric with said pivotal connection.

5. The combination of a cylinder, a rotary power shaft at the'axis of said cylinder, an eccentric arranged in said cylinder and fixed to said shaft, an annular piston mounted on said eccentric so as to contact with the circular inner face of the cylinder, said annular piston being smaller in diameter than said circular inner face, a pivotally supported abutment head movable into and out of said cylinder, said abutment head and piston being co-extensive relative to the axis of the cylinder, and a pivotal connection whereby said annular iston is connected to said abutment head,sai cylinder having inlet and outlet ports at opposite sides of said abutment head, said cylinder also having fixed inlet and outlet valve elements which project into the cylinder at points adjacent to said ports, said annular piston having valve elements formed within the circumferential line of the piston so as to cooperate with the first mentioned valve elements in opening and closing the ports, and the cooperating faces of the several valve elements being approximately concentric with said pivotal connection. I

In testimony that I claim the foregoing I hereunto afiix my signature.

GEORGE F. MOORS 

